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WO2003001129A1 - Dispositif frigorifique - Google Patents

Dispositif frigorifique Download PDF

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Publication number
WO2003001129A1
WO2003001129A1 PCT/JP2002/006373 JP0206373W WO03001129A1 WO 2003001129 A1 WO2003001129 A1 WO 2003001129A1 JP 0206373 W JP0206373 W JP 0206373W WO 03001129 A1 WO03001129 A1 WO 03001129A1
Authority
WO
WIPO (PCT)
Prior art keywords
compressor
heat exchanger
refrigerant
cooling
refrigeration
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2002/006373
Other languages
English (en)
Japanese (ja)
Inventor
Kenji Tanimoto
Masaaki Takegami
Takeo Ueno
Kazuyoshi Nomura
Akihiro Kajimoto
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Daikin Industries Ltd
Original Assignee
Daikin Industries Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Daikin Industries Ltd filed Critical Daikin Industries Ltd
Priority to EP02743722A priority Critical patent/EP1400766B1/fr
Priority to DE60233567T priority patent/DE60233567D1/de
Priority to KR1020037002826A priority patent/KR100544983B1/ko
Priority to JP2003507483A priority patent/JP3953029B2/ja
Priority to US10/362,625 priority patent/US6698217B2/en
Priority to AU2002346214A priority patent/AU2002346214B2/en
Publication of WO2003001129A1 publication Critical patent/WO2003001129A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B29/00—Combined heating and refrigeration systems, e.g. operating alternately or simultaneously
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/005—Arrangement or mounting of control or safety devices of safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/075—Details of compressors or related parts with parallel compressors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/22—Refrigeration systems for supermarkets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/06—Damage
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/021—Inverters therefor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/02—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures
    • F25D11/022—Self-contained movable devices, e.g. domestic refrigerators with cooling compartments at different temperatures with two or more evaporators
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B40/00—Technologies aiming at improving the efficiency of home appliances, e.g. induction cooking or efficient technologies for refrigerators, freezers or dish washers

Definitions

  • the present invention relates to a refrigeration apparatus, and more particularly, to a refrigeration apparatus including a heat exchanger for air conditioning and a heat exchanger for cooling. Thread
  • refrigeration systems have been widely used as air conditioners for cooling and heating the inside of a room, and as refrigerators for storing foods and the like.
  • Some refrigeration systems perform both air conditioning and refrigeration, as disclosed in WO98 / 45655.
  • This type of refrigeration equipment is installed in places where both air conditioning and refrigeration are required, for example, in convenience stores, etc., and uses multiple compressors and multiple heat exchangers such as air conditioning heat exchangers and refrigeration heat exchangers. Side heat exchanger. Therefore, by using this type of refrigeration system, the air conditioning in the store and the cooling of the showcase can be performed by one refrigeration system.
  • the capacity of either the air conditioning heat exchanger or the refrigeration heat exchanger decreases, or the capacity of both heat exchangers decreases. There was a tendency to decrease.
  • maintaining refrigeration capacity is more important than maintaining air conditioning capacity. This is because a decrease in air-conditioning capacity only causes occupants to feel uncomfortable, but a decrease in refrigeration capacity causes a decrease in the quality of objects to be cooled (for example, frozen foods).
  • the conventional refrigeration system was not configured to change the operation content to ensure the refrigeration capacity when a compressor failure occurred. Therefore, even if one compressor fails, operation can be continued while securing refrigeration capacity. There is a demand for a refrigerating device.
  • the present invention has been made in view of such a point, and an object of the present invention is to provide a refrigeration apparatus that can continue operation as it is even if one compressor fails. Disclosure of the invention
  • the first refrigeration system includes first, second, and third compressors provided in parallel with each other, a heat source-side heat exchanger, an air-conditioning heat exchanger for air-conditioning the room, and cooling the inside of the refrigerator.
  • a heat exchanger for cooling a refrigerant circuit having first and second expansion mechanisms for expanding the refrigerant, and at least a failure detecting means for detecting a failure of the second compressor.
  • a refrigeration operation of condensing a refrigerant in the heat source side heat exchanger, expanding the refrigerant in the second expansion mechanism, evaporating the refrigerant in the cooling heat exchanger, and returning the refrigerant to the first compressor and the second compressor is performed.
  • a flexible refrigeration apparatus that, when a failure of the second compressor is detected during the cooling operation, continues the cooling operation by operating the first compressor instead of the second compressor. You.
  • the second refrigeration system includes first, second and third compressors provided in parallel with each other, a heat source side heat exchanger, an air conditioning heat exchanger for air-conditioning the room, and cooling the inside of the refrigerator.
  • a heat exchanger for cooling a refrigerant circuit having first and second expansion mechanisms for expanding the refrigerant, and at least a failure detecting means for detecting a failure of the second compressor.
  • a refrigeration operation performed by operating a compressor and the second compressor, wherein the refrigerant discharged from the first compressor and the second compressor is condensed in the heat source side heat exchanger;
  • a refrigerating operation in which the refrigerant is expanded by an expansion mechanism, evaporated in the cooling heat exchanger, and returned to the first compressor and the second compressor; and the first compressor, the second compressor, and the third compressor.
  • a refrigeration apparatus capable of at least freely performing a cooling refrigeration operation in which the pressure is reduced to a second low pressure lower than the low pressure, evaporated in the cooling heat exchanger, and returned to the first compressor and the second compressor.
  • the refrigerant circuit includes: a refrigerant pipe that guides refrigerant from suction pipes of the first compressor and the second compressor toward a suction pipe of the third compressor; and a refrigerant pipe provided in the refrigerant pipe. Enclosing means, the second compression during the refrigeration operation. When the failure of the compressor is detected, the refrigeration operation is continued by opening the flow passage opening / closing means and operating the third compressor instead of the second compressor.
  • the third refrigeration system includes first, second, and third compressors provided in parallel with each other, a heat source-side heat exchanger, an air-conditioning heat exchanger for air-conditioning the room, and cooling the inside of the refrigerator.
  • a heat exchanger for cooling a refrigerant circuit having first and second expansion mechanisms for expanding the refrigerant, and at least a failure detecting means for detecting a failure of the second compressor.
  • a refrigeration operation performed by operating a compressor and the second compressor, wherein the refrigerant discharged from the first compressor and the second compressor is condensed in the heat source side heat exchanger;
  • a refrigerating operation in which the refrigerant is expanded by an expansion mechanism, evaporated in the cooling heat exchanger, and returned to the first compressor and the second compressor; and the first compressor, the second compressor, and the third compressor.
  • a cooling and refrigeration operation performed by operating the first compressor and the second compressor.
  • the refrigerant discharged from the third compressor is condensed in the heat source side heat exchanger, and a part of the condensed refrigerant is reduced to a first low pressure by the first expansion mechanism.
  • a refrigeration apparatus capable of at least freely performing a cooling refrigeration operation for returning to the first compressor and the second compressor, wherein the refrigerant circuit includes suction-side piping of the first compressor and the second compressor.
  • a refrigerant pipe for guiding the refrigerant from the third compressor to a suction side pipe of the third compressor; Further comprising means for closing the flow path, wherein when the failure of the second compressor is detected during the cooling / refrigeration operation, the flow path opening / closing means is opened, and the first compressor and the third compressor are opened.
  • the refrigerant discharged from the heat source side heat exchanger is condensed in the heat source side heat exchanger, and the pressure is reduced to a predetermined pressure lower than the first low pressure by the first expansion mechanism and the second expansion mechanism, respectively.
  • the cooling and refrigeration operation is continued by evaporating each of them in the heat exchanger and the cooling heat exchanger and returning them to the first compressor and the third compressor.
  • the fourth refrigeration system includes first, second, and third compressors provided in parallel with each other, a heat source-side heat exchanger, an air-conditioning heat exchanger for air-conditioning the room, and cooling the inside of the refrigerator.
  • a heat exchanger for cooling a refrigerant circuit having first and second expansion mechanisms for expanding the refrigerant, and at least a failure detecting means for detecting a failure of the third compressor.
  • a refrigeration operation performed by operating a compressor and the second compressor, wherein the refrigerant discharged from the first compressor and the second compressor is condensed in the heat source side heat exchanger;
  • a refrigerating operation in which the refrigerant is expanded by an expansion mechanism, evaporated in the cooling heat exchanger, and returned to the first compressor and the second compressor; and the first compressor, the second compressor, and the third compressor.
  • a cooling and refrigeration operation performed by operating the first compressor and the second compressor.
  • the refrigerant discharged from the third compressor is condensed in the heat source side heat exchanger, and a part of the condensed refrigerant is reduced to a first low pressure by the first expansion mechanism.
  • a refrigeration apparatus that is capable of at least freely performing a cooling refrigeration operation for returning to the first compressor and the second compressor, wherein the refrigerant circuit is connected to the first compressor from a suction side pipe of the third compressor.
  • a refrigerant pipe that guides refrigerant toward a suction-side pipe of the second compressor; and a flow path opening / closing means provided in the refrigerant pipe, wherein a failure of the third compressor during the cooling / refrigeration operation is performed.
  • the flow path opening / closing means Upon detection, the flow path opening / closing means is opened, and Refrigerant discharged from the first compressor and the second compressor is condensed by the heat source side heat exchanger, and the predetermined pressures lower than the first low pressure are respectively reduced by the first expansion mechanism and the second expansion mechanism. And evaporate in the air-conditioning heat exchanger and the cooling heat exchanger, respectively. By returning to the compressor, the cooling / refrigerating operation is continued.
  • the fifth refrigeration system includes first, second, and third compressors provided in parallel with each other, a heat source side heat exchanger, an air conditioning heat exchanger for air-conditioning the room, and cooling the inside of the refrigerator.
  • a heat exchanger for cooling a refrigerant circuit having first and second expansion mechanisms for expanding the refrigerant, and at least a failure detecting means for detecting a failure of the second compressor.
  • An operation wherein discharge is performed from the first compressor and the second compressor. At least, a refrigeration operation of condensing a refrigerant in the heat source side heat exchanger, expanding the refrigerant in the second expansion mechanism, evaporating the refrigerant in the cooling heat exchanger, and returning the refrigerant to the first compressor and the second compressor is performed.
  • a refrigeration apparatus that, when a failure of the second compressor is detected during the heating operation, continues the heating operation by operating the first compressor instead of the second compressor. You.
  • the sixth refrigeration system includes first, second, and third compressors provided in parallel with each other, a heat source side heat exchanger, an air conditioning heat exchanger for air-conditioning the room, and cooling the inside of the refrigerator.
  • a heat exchanger for cooling a refrigerant circuit having first and second expansion mechanisms for expanding the refrigerant, and at least a failure detecting means for detecting a failure of the second compressor.
  • a refrigeration operation wherein discharge from the first compressor and the second compressor is performed. While a part of the refrigerant is condensed in the air-conditioning heat exchanger, another discharged refrigerant is condensed in the heat source side heat exchanger, and both refrigerants are expanded by the second expansion mechanism.
  • a refrigeration system capable of at least freely performing a heating and refrigeration operation of evaporating in the heat exchanger and returning to the first compressor and the second compressor.
  • a refrigerant pipe that guides refrigerant from suction-side pipes of the first compressor and the second compressor toward a suction-side pipe of the third compressor; And a flow path opening / closing means provided, and when a failure of the second compressor is detected during the heating / refrigeration operation, the flow path opening / closing means is opened and the above-mentioned second compressor is substituted for the second compressor.
  • the heating and refrigeration operation is continued by operating the third compressor.
  • the cooling heat exchanger includes a refrigeration heat exchanger and a refrigeration heat exchanger
  • the refrigerant circuit includes the refrigeration heat exchanger.
  • an auxiliary compressor that is provided downstream of the compressor and lowers the refrigerant pressure in the refrigerating heat exchanger than the refrigerant pressure in the refrigerating heat exchanger.
  • An eighth refrigerating apparatus according to the seventh refrigerating apparatus, wherein one end is connected to a discharge side of the auxiliary compressor (53) and the other end is connected to a suction side of the auxiliary compressor (53).
  • the first compressor In the first refrigeration system, if the second compressor fails during the cooling operation, the first compressor is driven instead.
  • the refrigerant discharged from the first compressor and the third compressor condenses in the heat source side heat exchanger, expands in the first expansion mechanism, evaporates in the air conditioner heat exchanger, and evaporates in the first compressor and the third compressor. 3 Perform circulation operation returning to the compressor. As a result, the cooling operation can be continued while maintaining the cooling capacity.
  • the flow passage opening / closing means opens, and the third compressor is driven.
  • the refrigerant discharged from the first compressor and the third compressor condenses in the heat source side heat exchanger, expands in the second expansion mechanism, evaporates in the cooling heat exchanger, and A circulation operation to return to the third compressor is performed. As a result, the refrigeration operation can be continued while maintaining the refrigeration capacity.
  • the flow path opening / closing means opens.
  • the refrigerant discharged from the first compressor and the third compressor is condensed by the heat source side heat exchanger and decompressed by the first expansion mechanism and the second expansion mechanism, respectively. Circulation evaporates in the heat exchanger and returns to the first and third compressors Perform the operation. As a result, the refrigerant circulation amount of the cooling heat exchanger is maintained. On the other hand, the amount of refrigerant circulating in the air-conditioning heat exchanger decreases. However, since the refrigerant pressure in the air-conditioning heat exchanger decreases, the evaporation temperature of the solvent in the air-conditioning heat exchanger decreases.
  • the flow passage opening / closing means opens, and the refrigerant discharged from the first and second compressors passes through the heat source side heat exchanger. Condensed, decompressed by the first expansion mechanism and the second expansion mechanism, evaporated by the air-conditioning heat exchanger and the cooling heat exchanger, and returned to the first and second compressors. Do.
  • the cooling / refrigeration operation can be continued while at least maintaining the refrigeration capacity.
  • the first compressor is driven instead.
  • the refrigerant discharged from the first compressor and the third compressor is condensed in the air-conditioning heat exchanger, expanded in the first expansion mechanism, and evaporated in the heat source side heat exchanger. 3 Perform circulation operation returning to the compressor. As a result, the heating operation can be continued while maintaining the heating capacity.
  • the passage opening / closing means opens, and the third compressor is driven.
  • Some of the refrigerant discharged from the first and third compressors is condensed in the air-conditioning heat exchanger, while the other refrigerant is condensed in the heat source side heat exchanger, and both refrigerants are condensed in the second heat exchanger. 2Circulates by the expansion mechanism, evaporates in the cooling heat exchanger, and returns to the first and third compressors. As a result, the heating and refrigeration operation can be continued while maintaining at least the refrigeration capacity.
  • the cooling heat exchanger is equipped with two types of heat exchangers with different evaporation temperatures (refrigerating heat exchanger and refrigeration heat exchanger). Can be cooled.
  • the refrigerant bypasses the auxiliary compressor through the bypass passage, so that the flow of the refrigerant can be facilitated.
  • the predetermined operation can be continued without a large decrease in capacity. Therefore, the reliability of the device can be improved.
  • FIG. 1 is a refrigerant circuit diagram of the refrigeration apparatus.
  • FIG. 2 is a refrigerant circuit diagram showing the refrigerant circulation in the cooling operation.
  • FIG. 3 is a control flowchart of the cooling operation.
  • FIG. 4 is a diagram for explaining the first capacity control.
  • FIG. 5 is a refrigerant circuit diagram showing refrigerant circulation in a cooling operation when a compressor fails.
  • FIG. 6 is a diagram for explaining the second capacity control.
  • FIG. 7 is a refrigerant circuit diagram showing the refrigerant circulation in the refrigeration operation.
  • FIG. 8 is a control flowchart of the refrigeration operation.
  • FIG. 9 is a refrigerant circuit diagram showing refrigerant circulation in a refrigeration operation when a compressor fails.
  • FIG. 10 is a refrigerant circuit diagram showing the refrigerant circulation in the cooling and freezing operation.
  • FIG. 11 is a Mollier diagram illustrating a refrigeration cycle.
  • FIG. 12 is a refrigerant circuit diagram showing the refrigerant circulation in the cooling and freezing operation when the compressor fails.
  • FIG. 13 is a control flowchart of the cooling / refrigerating operation when the compressor fails.
  • FIG. 14 is a control flowchart of the cooling / refrigerating operation when the compressor fails.
  • FIG. 15 is a refrigerant circuit diagram showing the refrigerant circulation in the heating operation.
  • FIG. 16 is a control flowchart of the heating operation.
  • FIG. 17 is a refrigerant circuit diagram showing refrigerant circulation in a heating operation when a compressor fails.
  • FIG. 18 is a refrigerant circuit diagram showing the refrigerant circulation in the heating and refrigeration operation.
  • FIG. 19 is a control flowchart of the heating / freezing operation.
  • FIG. 20 is a refrigerant circuit diagram showing the refrigerant circulation in the heating and refrigeration operation when the compressor fails.
  • a refrigeration system (1) is a refrigeration system installed in a convenience store, which cools a showcase in a refrigerator and cools and heats a store in a room. It is for.
  • the refrigeration system (1) includes an outdoor unit (1A), an indoor unit (1B), a refrigeration unit (1C), and a refrigeration unit (1D), and includes a refrigerant circuit (1E) for performing a vapor compression refrigeration cycle. I have.
  • the indoor unit (1B) is configured to selectively perform a cooling operation and a heating operation, and is installed in, for example, a sales floor.
  • the refrigeration unit (1C) is installed in a refrigerated showcase and cools the air inside the showcase.
  • the refrigeration unit (1D) is installed in a freezer showcase and cools the air inside the showcase.
  • the outdoor unit (1A) includes a non-inverter overnight compressor (2A), a first invertor overnight compressor (2B) and a second invertime compressor (2C), and a first four-way switching valve (3A). And a second four-way switching valve (3B), and an outdoor heat exchanger (4) which is a heat source side heat exchanger.
  • Each compressor (2A, 2B 3 2C), for example, is composed of a hermetic high-pressure dome type scroll compressor.
  • the non-inverter compressor (2A) is of a fixed displacement type in which the motor is always driven at a constant speed.
  • the first Invar evening compressor (2B) and the second Invar evening compressor (2C) are compressors whose electric motors are controlled to be invar evening and whose capacity can be changed stepwise or continuously.
  • the non-inverter evening compressor (2A), the first invertor evening compressor (2B), and the second invar evening compressor (2C) have two systems of compression mechanisms, that is, the first system of compression mechanism (2D). Second series It constitutes a conventional compression mechanism (2E). The patterns of the compressors that compose these two systems of compression mechanisms (2D, 2E) are changed as appropriate.
  • the non-inverter evening compressor (2A) and the first invertor evening compressor (2B) constitute the first system compression mechanism (2D)
  • the second invar evening compressor (2C) constitutes the second system.
  • the non-inverter compressor (2A) constitutes the first system compression mechanism (2D)
  • the compressor (2C) forms the second system compression mechanism (2E).
  • Each discharge pipe (5a, 5b, 5c) of the non-inverter compressor (2A), the first inverter compressor (2B) and the second inverter compressor (2C) is connected to one high-pressure gas pipe (8 ), And the high-pressure gas pipe (8) is connected to the first port of the first four-way switching valve (3A).
  • the discharge pipe (5a) of the non-inverter compressor (2A), the discharge pipe (5b) of the first invertor compressor (2B), and the second invertor compressor so that they can be started by any compressor.
  • the discharge pipe (5c) of the compressor (2C) is provided with a check valve (7).
  • the gas side end of the outdoor heat exchanger (4) is connected to the second port of the first four-way switching valve (3A) by the outdoor gas pipe (9).
  • One end of a liquid pipe (10), which is a liquid line, is connected to the liquid side end of the outdoor heat exchanger (4).
  • a receiver (14) is provided in the middle of the liquid pipe (10), and the other end of the liquid pipe (10) branches to the first connecting liquid pipe (11) and the second connecting liquid pipe (12). are doing.
  • the type of the outdoor heat exchanger (4) is not particularly limited, and for example, a cross-fin type fin 'and' tube type heat exchanger or the like can be suitably used.
  • An outdoor fan (4F) is located near the outdoor heat exchanger (4).
  • suction pipes (6a, 6b) of the non-inverter overnight compressor (2A) and the first invar evening compressor (2B) are connected to the low-pressure gas pipe (15).
  • the suction pipe (6c) of the second inverter compressor (2C) is connected to the third port of the second four-way switching valve (3B).
  • the connecting gas pipe (17) is connected to the fourth port of the first four-way switching valve (3A).
  • the third port of the first four-way switching valve (3A) is connected to the fourth port of the second four-way switching valve (3B) by a connection pipe (18).
  • the first port of the second four-way switching valve (3B) is an auxiliary gas pipe (19) is connected to the discharge pipe (5c) of the second inverter compressor (2C).
  • the second port of the second four-way switching valve (3B) is a closed port that is always closed. That is, the second four-way switching valve (3B) is a flow path switching valve that appropriately connects the three ports. Therefore, it is also possible to use a three-way switching valve instead of the second four-way switching valve (3B).
  • the first four-way switching valve (3A) is in a first state in which the high-pressure gas pipe (8) communicates with the outdoor gas pipe (9) and the connection pipe (18) communicates with the communication gas pipe (17) (FIG.
  • the second four-way switching valve (3B) communicates with the auxiliary gas pipe (19) and the closing port, and connects with the connection pipe (18) and the suction pipe (6c) of the second inverter compressor (2C). 1 (see the solid line in FIG. 1), the second state in which the auxiliary gas pipe (19) communicates with the connecting pipe (18), and the second state in which the suction pipe (6c) communicates with the blocking port (FIG. 1). (See broken line).
  • the discharge pipes (5a, 5b, 5c), the high-pressure gas pipe (8), and the outdoor gas pipe (9) constitute a high-pressure gas line (1L) during cooling operation.
  • the low-pressure gas pipe (15) and each suction pipe (6a, 6b) of the first system compression mechanism (2D) constitute a first low-pressure gas line (1M).
  • the communication gas pipe (17) and the suction pipe (6c) of the second compression mechanism (2E) constitute a second low-pressure gas line (1N) during cooling operation.
  • the first connecting liquid pipe (11), the second connecting liquid pipe 2 ), the connecting gas pipe (17) and the low-pressure gas pipe (15) are extended from the outdoor unit (1A) to the outside, and each of the outdoor units (1A) is extended.
  • a closing valve (20) is provided in).
  • a check valve (7) is provided in the outdoor unit (1A) at the branch end of the second communication liquid pipe (12), and refrigerant flows from the receiver (14) to the shutoff valve (20). It is configured to flow.
  • the communication pipe (21) enables communication between the suction sides of the non-inverter compressor (2A), the first invertor compressor (2B), and the second inverer compressor (2C).
  • the communication pipe (21) branches off from the main pipe (22) and the main pipe (22).
  • a first sub-tube (23) and a second sub-tube (24) are provided.
  • the main pipe (22) is connected to the suction pipe (6c) of the second invertor compressor (2C).
  • the first sub pipe (23) and the second sub pipe (24) are connected to the low pressure gas pipe (15).
  • Each of the first sub-tube (23) and the second sub-tube (24) is provided with a solenoid valve (7a, 7b) and a check valve (7) as opening / closing mechanisms.
  • the first sub pipe (23) runs from the suction pipe of the non-inverter compressor (2A) and the first inverter compressor (2B) to the suction pipe of the second inverter compressor (2C). It is configured to circulate a refrigerant.
  • the second sub pipe (24) transfers refrigerant from the suction pipe of the second inverter compressor (2C) to the suction pipe of the non-inverter compressor (2A) and the first inverter compressor (2B). It is configured to be distributed.
  • An auxiliary liquid pipe (25) that bypasses the receiver (14) is connected to the liquid pipe (10).
  • the refrigerant mainly flows during heating in the auxiliary liquid pipe (25), and the auxiliary liquid pipe (25) is provided with an outdoor expansion valve (26) as an expansion mechanism.
  • a check valve (7) is provided between the outdoor heat exchanger (4) and the receiver (14) in the liquid pipe (10) to allow only the refrigerant flow toward the receiver (14).
  • the check valve (7) is located between the connection of the auxiliary liquid pipe (25) in the liquid pipe (10) and the receiver (14).
  • auxiliary liquid pipe (2 5) low-pressure gas pipe (15)
  • Riki Uz de injection pipe (27) is connected between the auxiliary liquid pipe (2 5) low-pressure gas pipe (15).
  • the liquid injection pipe (27) is provided with a solenoid valve (7c).
  • a degassing pipe (28) is connected between the upper part of the receiver (14) and the discharge pipe (5a) of the non-inverter compressor (2A).
  • the gas vent pipe (28) is provided with a check valve (7) that allows only the refrigerant flow from the receiver (14) to the discharge pipe (5a).
  • the high-pressure gas pipe (8) is provided with an oil separator (30). One end of an oil return pipe (31) is connected to the oil separator (30).
  • the oil return pipe (31) is provided with a solenoid valve (7d), and the other end of the oil return pipe (31) is connected to the suction pipe (6a) of the non-inverter compressor (2A).
  • the first oil level equalizing pipe (3 2) is connected between the intake pipe of non-inverting evening compressor dome and second inverter Isseki compressors of (2A) (2C) (6c).
  • the oil pipe (32) is provided with a check valve (7) and a solenoid valve (7e) that allow oil flow from the non-inverter compressor (2A) to the second invar compressor (2C). I have.
  • One end of a second oil leveling pipe (33) is connected to the dome of the first Invar evening compressor (2B).
  • the other end of the second oil leveling pipe (33) is connected between the check valve (7) and the solenoid valve (7e) of the first oil leveling pipe (32).
  • a third oil equalizing pipe (34) is connected between the dome of the second invar overnight compressor (2C) and the low-pressure gas pipe (15).
  • the third oil leveling pipe (34) is provided with an electromagnetic valve (7f).
  • a floor heating circuit (35) is connected to the liquid pipe (10).
  • the floor heating circuit (35) includes a floor heating heat exchanger (36), a first pipe (37), and a second pipe (38).
  • One end of the first pipe (37) is connected between the check valve (7) and the closing valve (20) in the first connecting liquid pipe (11), and the other end is a floor heating heat exchanger (36). It is connected to the.
  • One end of the second pipe (38) is connected between the check valve (7) and the receiver (14) in the liquid pipe (10), and the other end is connected to the floor heating heat exchanger (36).
  • the floor heating heat exchanger (36) is located in a convenience store, at a cash register where cashiers work long hours.
  • the first pipe (37) and the second pipe (38) are provided with a shutoff valve (20), and the first pipe (37) allows only the refrigerant flow toward the floor heating heat exchanger (36).
  • Check valve (7) is provided.
  • the floor heating heat exchanger (36) can be reduced. If the floor heating heat exchanger (36) is not provided, the first pipe (37) and the second pipe (38) are directly connected. Connected.
  • the indoor unit (1B) includes an indoor heat exchanger (41) as a use side heat exchanger and an indoor expansion valve (42) as an expansion mechanism.
  • the connecting gas pipe (17) is connected to the gas side of the indoor heat exchanger (41).
  • the liquid side of the indoor heat exchanger (41) is connected to a second communication liquid pipe (12) via an indoor expansion valve (42).
  • the type of the indoor heat exchanger (41) is not particularly limited, and for example, a cross-fin type fin-and-tube heat exchanger can be suitably used.
  • an indoor fan (43) which is a use-side fan, is arranged.
  • the refrigeration unit (1C) includes a refrigeration heat exchanger (45) as a cooling heat exchanger and a refrigeration expansion valve ( 46 ) as an expansion mechanism.
  • the liquid side of the refrigerating heat exchanger (4 5), the first communication liquid pipe via a solenoid valve () ⁇ beauty refrigerating expansion valve (46) (11) is connected.
  • a low-pressure gas pipe (15) is connected to the gas side of the refrigeration heat exchanger (45).
  • the refrigeration heat exchanger (45) communicates with the suction side of the first-stage compression mechanism (2D), while the indoor heat exchanger (41) communicates with the suction side of the second inverter compressor (2C) during cooling operation.
  • the refrigerant pressure (evaporation pressure) of the refrigeration heat exchanger (45) is usually lower than the refrigerant pressure (evaporation pressure) of the indoor heat exchanger (41).
  • the refrigerant evaporation temperature of the refrigeration heat exchanger (45) is, for example, ⁇ 10 ° C.
  • the refrigerant evaporation temperature of the indoor heat exchanger (41) is, for example, + 5 ° C.
  • the refrigerant circuit (1E) constitutes a so-called different temperature evaporation circuit.
  • the refrigeration expansion valve (46) is a temperature-sensitive expansion valve, and a temperature-sensitive cylinder is attached to the gas side of the refrigeration heat exchanger (45).
  • a temperature-sensitive cylinder is attached to the gas side of the refrigeration heat exchanger (45).
  • the refrigeration heat exchanger (45) for example, a cross-fin type fin-and-tube heat exchanger can be suitably used.
  • the refrigeration unit (1D) includes a refrigeration heat exchanger (51) as a cooling heat exchanger, a refrigeration expansion valve (52) as an expansion mechanism, and a booth-type compressor (53) as a refrigeration compressor. ing.
  • a branch liquid pipe (13) branched from the first communication liquid pipe (11) is connected to the liquid side of the refrigeration heat exchanger (51) via an electromagnetic valve (7h) and a refrigeration expansion valve (52). ing.
  • the gas side of the refrigeration heat exchanger (51) and the suction side of the booth compressor (53) are connected by a connecting gas pipe (54).
  • a branch gas pipe (16) branched from the low-pressure gas pipe (15) is connected to the discharge side of the booth compressor (53).
  • the branch gas pipe (16) is provided with a check valve (7) and an oil separator (55).
  • An oil return pipe (57) having a capillary tube (56) is connected between the oil separator (55) and the connecting gas pipe (54).
  • the refrigerant evaporation temperature of the refrigeration heat exchanger (51) The refrigerant is two-stage compressed together with the first-stage compression mechanism (2D) so as to be lower than the refrigerant evaporation temperature.
  • the refrigerant evaporation temperature of the refrigeration heat exchanger (51) is set to, for example, ⁇ 40 ° C.
  • the refrigeration expansion valve (52) is a temperature-sensitive expansion valve, and a temperature-sensitive cylinder is attached to the gas side of the refrigeration heat exchanger (51).
  • a refrigeration heat exchanger (51) for example, a cross fin type fin 'and' tube type heat exchanger can be suitably used.
  • a refrigeration fan (58) which is a cooling fan, is arranged in close proximity.
  • connection gas pipe (54), which is the suction side of the booth and evening compressor (53), and the branch gas pipe (16), which is the discharge side of the booth and evening compressor (53), are located downstream of the check valve (7).
  • a bypass pipe (59) having a check valve (7) is connected between them.
  • the bypass pipe (59) flows the refrigerant so as to bypass the booth evening compressor (53) when the booth evening compressor (53) stops due to a failure or the like.
  • the refrigerant circuit (1E) is provided with various sensors and various switches.
  • the high-pressure gas pipe (8) of the outdoor unit (1A) has a high-pressure pressure sensor (61) as pressure detection means for detecting high-pressure refrigerant pressure and a discharge temperature sensor (temperature) as temperature detection means for detecting high-pressure refrigerant temperature. 62).
  • the discharge pipe (5c) of the second inverter compressor (2C) is provided with a discharge temperature sensor (63) as temperature detecting means for detecting the high-pressure refrigerant temperature.
  • a high-pressure refrigerant pressure is applied to the discharge pipes (5a, 5b, 5c) of the non-inverter compressor (2A), the first invertor compressor (2B), and the second inverer compressor (2C).
  • a pressure switch (64) is provided that is activated above the value.
  • Each of the suction pipes (6b, 6c) of the first Invar evening compressor (2B) and the second Invar evening compressor (2C) has a low pressure pressure sensor (65, 66) serving as a pressure detecting means for detecting a low pressure refrigerant pressure. And a suction temperature sensor (67, 68) as temperature detecting means for detecting the low-pressure refrigerant temperature.
  • the outdoor heat exchanger (4) is provided with an outdoor heat exchange temperature sensor (69) as temperature detecting means for detecting an evaporation temperature or a condensation temperature as a refrigerant temperature in the outdoor heat exchanger (4).
  • the outdoor unit (1A) is provided with an outdoor air temperature sensor (70) as a temperature detecting means for detecting the outdoor air temperature.
  • the indoor heat exchanger (41) is provided with an indoor heat exchange temperature sensor (71) as temperature detecting means for detecting a condensing temperature or an evaporating temperature which is a refrigerant temperature in the indoor heat exchanger (41).
  • an indoor heat exchange temperature sensor (71) as temperature detecting means for detecting a condensing temperature or an evaporating temperature which is a refrigerant temperature in the indoor heat exchanger (41).
  • a gas temperature sensor (72) as temperature detecting means for detecting a gas refrigerant temperature is provided on the gas side of the indoor heat exchanger (41).
  • the indoor unit (1B) is provided with a room temperature sensor (73) as temperature detecting means for detecting the indoor air temperature.
  • the refrigeration unit (1C) is provided with a refrigeration temperature sensor (74) which is a temperature detecting means for detecting the temperature in the refrigerator in the refrigerated showcase.
  • the refrigeration unit (1D) is provided with a refrigeration temperature sensor (75) which is a temperature detecting means for detecting the temperature in the refrigerator inside the freezer showcase.
  • the second pipe (38) of the floor heating circuit (35) is provided with a liquid temperature sensor (76) that is a temperature detecting means for detecting a refrigerant temperature after flowing through the floor heating heat exchanger (36). .
  • Output signals of various sensors and various switches are input to the controller (80).
  • the controller (80) is configured to control the capacity and the like of the first inverter compressor (2B) and the second inverter compressor (2C).
  • the controller (80) has a failure detection unit that detects a failure of each of the compressors (2A, 2B, 2C).
  • the failure detection of the compressor a known technique can be used.
  • the failure can be detected based on the overcurrent of each compressor (2A, 2B, 2C), the temperature of the discharged refrigerant, and the like.
  • the method of determining the failure There is no particular limitation on the method of determining the failure.
  • the failure may be determined if the abnormality related to the compressor occurs five times consecutively at the time of startup.
  • the controller (80) is configured to execute not only the above-described compressor failure detection, but also the following various operations, and also perform switching control of those operations.
  • the cooling operation is an operation for cooling only the indoor unit (1B).
  • the non-inverter overnight compressor (2A) forms the first system compression mechanism (2D), and the first invertor overnight compressor (2B) and the second invertor compressor (2B).
  • the second night compressor (2C) Configure the compression mechanism (2E). Then, only the first invertor compressor (2B) and the second invertor compressor (2C), which are the second-system compression mechanisms (2E), are driven.
  • the first four-way switching valve (3A) and the second four-way switching valve (3B) switch to the first state as shown by the solid line in FIG.
  • the solenoid valve (7b) of the second sub pipe (24) of the communication pipe (21) is open.
  • the solenoid valve (7a) of the first auxiliary pipe (23) of the communication pipe (21), the outdoor expansion valve (26), the solenoid valve ( 7 g ) of the refrigerator unit (1C), and the solenoid valve (7D) of the refrigeration unit (1D) 7h) is closed.
  • the refrigerant discharged from the first invar and evening compressors (2B) and the second invar and evening compressors (2C) passes through the outdoor gas pipe (9) from the first four-way switching valve (3A) through the outdoor gas pipe (9). It flows into the heat exchanger (4) and condenses in the outdoor heat exchanger (4).
  • the condensed liquid refrigerant flows through the liquid pipe (10), flows through the second connecting liquid pipe (12) via the receiver (14), expands at the indoor expansion valve (42), and evaporates at the indoor heat exchanger (41). I do.
  • the evaporated gas refrigerant passes through the connecting gas pipe (17), passes through the first four-way switching valve (3A) and the second four-way switching valve (3B), and enters the suction pipe (6c) of the second inverter compressor (2C). And return to the 1st inver / night compressor (2B) and 2nd invar / evening compressor (2C). Such refrigerant circulation is repeated, and the inside of the store, which is a room, is cooled.
  • step ST11 it is determined whether or not the condition 1 that the room temperature Tr detected by the room temperature sensor (73) is higher than the temperature obtained by adding 3 ° C to the set temperature Tset is satisfied.
  • step ST12 it is determined whether or not the condition 2 that the room temperature Tr is lower than the set temperature Tset is satisfied. If the condition 1 of step ST11 is satisfied, the process proceeds to step ST13, in which the capacity of the first inverter compressor (2B) or the second inverter compressor (2C) is increased and the return is performed. On.
  • step ST 11 If the condition 1 of step ST 11 above is not satisfied and the condition 2 of step ST 1 2 is satisfied, the process proceeds to step ST 14 and the first inverter compressor (2B) or the second inverter compressor is used. Return with lower (2C) ability. If condition 2 of step ST 1 2 above is not satisfied, the current compression function is satisfied, so return. The above operation is repeated.
  • the capacity control of the compressor in steps ST13 and ST14 is performed as follows. That is, in the above-described control for increasing the compressor capacity, as shown in FIG. 4, first, one of the impeller compressors (here, the first invertor compressor (2B)) is switched from the stopped state to the minimum displacement. (See point A), while keeping this invertor compressor (2B) at the minimum capacity, the other invertor compressor (here, the second invertor compressor (2C)) is turned off. Drive and increase capacity. Thereafter, when the load further increases, the capacity of the first invertor overnight compressor (2B) is increased while keeping the second invar overnight compressor (2C) at the maximum capacity (see point B).
  • the reduction control of the compressor capacity is control performed in a procedure reverse to the above-described increase control.
  • the capacity control of the compressor that is, the capacity control when both compressors are invertor compressors, will be particularly referred to as “first capacity control”.
  • the degree of superheat of the indoor expansion valve (42) is controlled based on the temperatures detected by the indoor heat exchange temperature sensor (71) and the gas temperature sensor (72).
  • the controller (80) detects the failure and stops the operation of the compressor (2B). Then, the non-inverter overnight compressor (2A) that has not been operated is started. In other words, the non-inverter compressor (2A) is operated instead of the failed compressor (2B).
  • the refrigerant circulates as shown in FIG. That is, the refrigerant discharged from the non-inverter and second compressors (2A) and (2C) condenses in the outdoor heat exchanger (4), expands in the indoor expansion valve (42), and A circulation operation is performed in the exchanger (41), which evaporates and returns to the non-inverter compressor (2A) and the second inverer compressor (2C).
  • capacity control of the compressor is performed as follows. That is, Figure As shown in Fig. 6, when the load is light, the non-inverter overnight compressor (2A) is first stopped, and then the invar overnight compressor (in this operation, the second invar overnight compressor (2C)) is driven. (Refer to point A), increase the capacity. After the second inverter compressor (2C) rises to its maximum capacity (see point B), when the load further increases, the non-inverter compressor (2A) is driven and the second inverter compressor is simultaneously activated. Reduce (2C) to minimum capacity (see point C). Thereafter, when the load further increases, the capacity of the second chamber overnight compressor (2C) is increased.
  • the reduction control of the compressor capacity is performed in a procedure reverse to the above-described increase control.
  • the capacity control of the above-described compressor that is, the capacity control when one compressor is a non-inverter compressor and the other compressor is an invertor compressor, will be referred to as “second compressor”.
  • Capacity control ”.
  • the cooling operation is performed without stopping the cooling operation and without causing a shortage of the cooling capacity. Can be continued as it is.
  • the refrigeration operation is an operation that only cools the refrigeration unit (1C) and the refrigeration unit (1D).
  • the non-inverter evening compressor (2A) and the first invertor-evening compressor (2B) constitute a first-stage compression mechanism (2D), and the second invertor evening compressor (2D).
  • the compressor (2C) forms the second system compression mechanism (2E). Then, only the non-inverter compressor (2A) and the first invertor compressor (2B), which are the first-system compression mechanisms (2D), are driven, and the booth evening compressor (53) is also driven.
  • the first four-way switching valve (3A) switches to the first state as shown by the solid line in FIG.
  • the solenoid valve (7g) of the refrigeration unit (1C) and the solenoid valve (7h) of the refrigeration unit (1D) are open.
  • Two solenoid valves (7a, 7b), outdoor expansion valve (26) and indoor expansion valve (42) of communication pipe (21) are closed.
  • the other liquid refrigerant flowing through the first connecting liquid pipe (11) flows through the branch liquid pipe (13), passes through the refrigeration expansion valve (52), and evaporates in the refrigeration heat exchanger (51).
  • the gas refrigerant evaporated in the refrigerating heat exchanger (51) is sucked and compressed by the booster compressor (53) and discharged to the branch gas pipe (16).
  • the gas refrigerant evaporated in the refrigeration heat exchanger (45) and the gas refrigerant discharged from the booth compressor (53) are combined in the low-pressure gas pipe (15), and are combined into the non-inverter overnight compressor (2A) and the first impeller. — Return to the evening compressor (2B). Such a circulation operation is repeated to cool the inside of the refrigerator, which is a refrigeration showcase and a freezing showcase.
  • the refrigerant flowing out of the refrigeration heat exchanger (51) is sucked by the booth compressor (53).
  • the pressure becomes lower than the medium pressure.
  • the refrigerant temperature (evaporation temperature) in the refrigeration heat exchanger (51) becomes 140 ° C.
  • the refrigerant temperature (evaporation temperature) in the refrigeration heat exchanger (45) becomes ⁇ 10 ° C. Cooling will take place at different cooling temperatures.
  • step ST21 it is determined whether or not the condition 1 that the low-pressure refrigerant pressure LP detected by the low-pressure pressure sensors (65, 66) is higher than 392 kPa is satisfied.
  • step ST22 it is determined whether or not the condition 2 that the low-pressure refrigerant pressure LP is lower than 245 kPa is satisfied.
  • step ST21 If the condition 1 of step ST21 is satisfied, the process proceeds to step ST23, in which the capacity of the first invertor compressor (2B) or the non-inverter compressor (2A) is increased and the return is performed. . If the condition 1 of step ST 21 above is not satisfied and the condition 2 of step ST 22 is satisfied, the process proceeds to step ST 24 and the 1st invar overnight compressor (2B) or non-invar overnight compression Return with reduced capacity of machine (2A). Also, the provisions of step ST22 If condition 2 is not satisfied, the current compression function is satisfied, so the program returns and repeats the above operation.
  • the superheat degree is controlled by the temperature-sensitive cylinder.
  • the controller (80) detects the failure and stops the operation of the compressor (2B). Then, the second invar overnight compressor (2C), which has not been operated, is started and the solenoid valve (7a) is engaged. As a result, the refrigerant circulates as shown in FIG.
  • Non'inpa Yu ⁇ compressor (2 A) and a second inverter refrigerant discharged from Isseki compressor (2C) is condensed in the outdoor heat exchanger (4), cold storage expansion valve (46) and the freezing expansion valve It expands at that of (52) and evaporates at that of the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51) to the non-inverter compressor (2A) and the second inverer compressor (2C). Perform a return circulation operation. Regarding the control of the non-inverter overnight compressor (2A) and the second invar evening compressor (2C), the above-mentioned second capacity control is performed (see Fig. 6).
  • the controller (80) detects the failure and stops the operation of the compressor (2A). Then, the second invar overnight compressor (2C), which has not been operated, is started and the solenoid valve (7a) is opened.
  • the refrigerant discharged from the first and second inverter compressors (2B) and (2C) is condensed in the outdoor heat exchanger (4), and is cooled by the refrigeration expansion valve (46) and the refrigeration expansion. Expanded at each of the valves (52) and refrigerated heat exchangers (45) and refrigerated heat exchangers (51) The evaporator then circulates to return to the first chamber compressor (2B) and the second chamber compressor (2C).
  • the refrigeration operation can be continued without stopping the refrigeration operation and without causing a shortage of the refrigeration capacity.
  • the cooling and freezing operation is an operation that simultaneously cools the indoor unit (1B) and cools the refrigerator unit (1C) and the freezing unit (1D).
  • the non-inverter and evening compressor (2A) and the first invertor and evening compressor (2B) constitute the first system compression mechanism (2D)
  • the second The overnight compressor (2C) constitutes the second system compression mechanism (2E).
  • the non-inverter overnight compressor (2A), the first impeller evening compressor (2B) and the second inver evening compressor (2C) are driven, and the booth evening compressor (53) is also driven.
  • the first four-way switching valve (3A) and the second four-way switching valve (3B) are each switched to the first state as shown by the solid line in FIG.
  • the solenoid valve (7g) of the refrigeration unit (1C) and the solenoid valve (7h) of the refrigeration unit (1D) are open.
  • the two solenoid valves (7a, 7b) and the outdoor expansion valve (26) of the communication pipe (21) are closed.
  • the refrigerant discharged from the non-inverting compressor (2A), the first inverting compressor (2B), and the second inverting compressor (2C) merges in the high-pressure gas pipe (8), Condensed in the outdoor heat exchanger (4) from the four-way switching valve (3A) through the outdoor gas pipe (9).
  • the condensed liquid refrigerant flows through the liquid pipe (10), passes through the receiver (14), and flows into the first connecting liquid pipe (11) and the second connecting liquid pipe (12).
  • the liquid refrigerant flowing through the second communication liquid pipe (12) expands at the indoor expansion valve (42) and evaporates at the indoor heat exchanger (41).
  • the evaporated gas refrigerant flows from the connecting gas pipe (17), through the first four-way switching valve (3A) and the second four-way switching valve (3B), through the suction pipe (6c), and then through the second inverter compressor. Return to (2C).
  • part of the liquid refrigerant flowing through the first connecting liquid pipe (11) expands at the refrigeration expansion valve (46) and evaporates at the refrigeration heat exchanger (45).
  • Another liquid coolant flowing through the first connecting liquid pipe (11) flows through the branch liquid pipe (13), expands at the refrigeration expansion valve (52), and evaporates at the refrigeration heat exchanger (51). .
  • the gas refrigerant evaporated in the refrigerating heat exchanger (51) is sucked and compressed by the booster compressor (53) and discharged to the branch gas pipe (16).
  • Such a circulating operation is repeated to cool the interior of the store, which is indoors, and to cool each of the refrigerators, which is a showcase for refrigeration and a showcase for freezing.
  • Refrigerant drawn into the second inverter compressor (2C) is compressed to point A.
  • the refrigerant is compressed to the point B by the non-inverter compressor (2A) and the first inverter compressor (2B).
  • the refrigerant at point A and the refrigerant at point B merge and condense to become the refrigerant at point C.
  • Part of the refrigerant at point C is decompressed to point D by the indoor expansion valve (42), evaporates at, for example, + 5 ° C, and is sucked into the second inverter compressor (2C) at point E.
  • a part of the refrigerant at the point C is decompressed to the point F by the refrigerating expansion valve (46), evaporates at 110 ° C, for example, and the non-inverter compressor (2A) and the first It is sucked into the Imba overnight compressor (2B).
  • a part of the refrigerant at the point C is decompressed to the point H by the refrigerating expansion valve (52), evaporates at, for example, 140 ° C, and is sucked into the booth compressor (53) at the point I. .
  • the refrigerant compressed to point J by the booster compressor (53) is sucked into the non-inverter compressor (2A) and the first invertor compressor (2B) at point G.
  • the refrigerant in the refrigerant circuit (1E) is compressed by the first-stage compression mechanism (2D), the second-system compression mechanism (2E), and the booth compressor (53), for a total of three types of evaporation. Evaporates at temperature.
  • Cooling and refrigeration operation when one compressor fails In the present refrigeration system (1), if the non-inverter compressor (2A) or the first invertor compressor (2B) fails during the above-mentioned cooling / refrigeration operation, the solenoid valve (7a) of the first sub-pipe (23) is activated. Open the cooling refrigeration operation.
  • the controller (80) detects the failure and stops the operation of the compressor (2B). Then, the solenoid valve (7a) is opened. As a result, the refrigerant circulates as shown in FIG.
  • the refrigerant discharged from the non-inverter compressor (2A) and the second invertor compressor (2C) is condensed in the outdoor heat exchanger (4), is branched, and is then cooled by the indoor unit (1B).
  • the refrigerant flowing into the refrigeration unit (1C) and the refrigeration unit (1D) expands at the refrigeration expansion valve (46) and the refrigeration expansion valve (52), respectively, as in the cooling / refrigeration operation, and the refrigeration heat exchanger. (45) and in the refrigeration heat exchanger (51) evaporate separately.
  • the refrigerant flowing into the indoor unit (1B) expands at the indoor expansion valve (42) and evaporates at the indoor heat exchanger (41).
  • the solenoid valve (7a) since the solenoid valve (7a) is open, the suction side of the non-inverter overnight compressor (2A) and the suction side of the second invar overnight compressor (2C) are connected to the first sub pipe (23). Are communicated through Therefore, in this operation, the suction pressure of the non-inverter compressor (2A) is equal to the suction pressure of the second inverter compressor (2C). As a result, the refrigerant pressure of the indoor heat exchanger (41) is equal to the refrigerant pressure of the refrigeration heat exchanger (45), unlike the cooling and refrigeration operation when the compressor is not out of order.
  • the refrigerant evaporation temperature of the indoor heat exchanger (41) is equal to the refrigerant evaporation temperature of the refrigeration heat exchanger (45), and the cooling temperature of the indoor heat exchanger (41) is lower than before the compressor failure. Lower.
  • step ST51 the failure of the non-inverter compressor (2A) or the first inverter compressor (2B) is determined, and if the determination result is YES, the process proceeds to step ST52, where the solenoid valve is operated. (7a) is opened.
  • step ST53 a determination is made that the low-pressure refrigerant pressure LP is greater than 392 kPa. In the case of YES, the compression function is increased in step ST55, and the process returns.
  • step ST54 it is determined whether or not the low-pressure refrigerant pressure LP ⁇ 245 kPa. If YES, proceed to step ST56, reduce the compression function, and return. If the decision result in the step ST54 is NO, the process returns as it is.
  • step ST31 the failure of the second inverter compressor (2C) is determined, and if YES, the process proceeds to step ST32.
  • step ST32 it is determined whether or not the solenoid valve (7b) of the second sub pipe (24) is open. If the decision result in the step ST32 is NO, the process proceeds to a step ST33 to determine whether or not the low-pressure refrigerant pressure LP is higher than 392 kPa. If the result of the determination in step ST33 is N0, the process proceeds to step ST34, and it is determined whether the low-pressure refrigerant pressure LP is lower than 245 kPa. If the decision result in the step ST 34 is NO, the process returns.
  • step ST36 it is decided whether or not the condition of the room temperature Tr-set temperature Tset and 0 ° C is satisfied. As a result, in the case of YESS, it is determined that cooling is not necessary because the indoor temperature is lower than the set temperature, and the process proceeds to step ST42, where the solenoid valve (7b) is closed and the indoor expansion valve (42) is closed. And return. On the other hand, if the decision result in step ST36 is NO, the process proceeds to step ST37.
  • step ST37 the room temperature Tr-set temperature Tset> 3 ° C or low pressure refrigerant pressure L It is determined whether or not the condition of P> 392 kPa is satisfied. If the result of the determination is YES, the operation proceeds to step ST38, in which the capacity of the compressor is increased and the routine returns. If the decision result in the step ST 37 is NO, the process proceeds to a step ST 39 to determine whether or not the condition that the compression function force is the maximum and the low-pressure refrigerant pressure LP> 39 2 3 ⁇ 4: Pa is satisfied. . If the determination result in step ST39 is YES, the process proceeds to step ST42, and if the determination result in step ST39 is N0, the process returns.
  • step ST33 determines whether the determination result of step ST33 is YES. If the determination result of step ST33 is YES, the process proceeds to step ST40 to increase the capacity of the compressor and return. If the determination result in step ST34 is YES, the process proceeds to step ST41, where the solenoid valve (7b) is opened, and the process returns.
  • the heating operation is an operation that only heats the indoor unit (1B) and the floor heating circuit (35).
  • the non-inverter overnight compressor (2A) forms the first system compression mechanism (2D), and the first invertor compressor (2B) and the second invertor compressor (2B).
  • the nighttime compressor (2C) constitutes the second system compression mechanism (2E). Then, only the first invar / night compressor (2B) and the second invar / night compressor (2C), which are the second-system compression mechanisms (2E), are driven.
  • the first four-way switching valve (3A) switches to the second state, as shown by the solid line in FIG. 15, and the second four-way switching valve (3B), as shown by the solid line in FIG. Switch to the first state.
  • Communicating tube (2 1) second auxiliary pipe solenoid valve (24) in (7b) is opened.
  • Solenoid valve of the first sub-tube of the communication pipe (21) (2 3) solenoid valve (7a), the solenoid valve of the refrigerating Yunidzu bets (1C) (7 g) and refrigeration Yunidzu preparative (1D) (7h) is closed ing.
  • the refrigerant discharged from the first inverter compressor (2B) and the second inverter compressor (2C) passes through the connecting gas pipe (17) from the first four-way switching valve (3A) and enters the room. It condenses in the heat exchanger (41).
  • the condensed liquid refrigerant flows through the second connecting liquid pipe (12), It flows through the heating circuit (35) and then through the floor heating heat exchanger (36) to the receiver (14). Thereafter, the liquid refrigerant evaporates in the outdoor heat exchanger (4) through the outdoor expansion valve (26) of the auxiliary liquid pipe (25).
  • the evaporated gas refrigerant passes through the first four-way switching valve (3A) and the second four-way switching valve (3B), flows through the suction pipe (6c) of the second invertor compressor (2C), and flows through the first invertor. Return to the evening compressor (2B) and the second inver evening compressor (2C). This circulation is repeated, and the inside of the store, which is the room, is heated and the floor is heated.
  • step ST61 it is determined whether or not the condition 1 that the set temperature Tset—the indoor temperature Tr> 3 ° C is satisfied.
  • step ST62 it is determined whether or not the condition 2 of the set temperature Tset—the indoor temperature Tr is 0 ° C is satisfied.
  • step ST61 the process proceeds to step ST63, in which the capacity of the first inverter compressor (2B) or the second inverter compressor (2C) is increased and the process returns. . If the condition 1 in step ST61 above is not satisfied and the condition 2 in step ST62 is satisfied, the process proceeds to step ST64, where the first invar overnight compressor (2B) or the second invertor is used. Evening compressor (2C) 's capacity is reduced and returns. If the condition 2 of step ST62 above is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated. When increasing or decreasing the compressor capacity, the first capacity control described above is performed (see Fig. 4).
  • the degree of opening of the outdoor expansion valve (26) is controlled based on the superheat degree based on the saturation temperature corresponding to the pressure based on the low-pressure pressure sensors (65, 66) and the temperature detected by the suction temperature sensors (67, 68).
  • the degree of opening of the indoor expansion valve (42) is supercooled based on the temperatures detected by the indoor heat exchange temperature sensor (71) and the liquid temperature sensor (76).
  • the refrigerant discharged from the non-inverter compressor (2A) and the second inverer compressor (2C) condenses in the indoor heat exchanger (41) and the floor heating heat exchanger (36), and the outdoor expansion valve It expands in (26), evaporates in the outdoor heat exchanger (4), and returns to the non-inverter compressor (2A) and the second inverer compressor (2C).
  • the second displacement control is executed to increase or decrease the capacity of the compressor in this operation (see Fig. 6).
  • the heating operation can be performed without stopping the heating operation and without causing a shortage of the heating capacity. Can be continued as it is.
  • the non-inverter evening compressor (2A) and the first invertor evening compressor (2B) constitute the first system compression mechanism (2D), and the The evening compressor (2C) constitutes the second system compression mechanism (2E). Then, the non-inverter overnight compressor (2A) and the first Inver night compressor (2B) are driven, and the booth evening compressor (53) is also driven. The operation of the above-mentioned No. 2 Invar evening compressor (2C) has been stopped.
  • the first four-way switching valve (3A) switches to the second state, as shown by the solid line in FIG. 18, and the second four-way switching valve (3B), as shown by the solid line in FIG. Switch to the second state.
  • the solenoid valve (7g) of the refrigerator unit (1C) and the solenoid valve (7h) of the refrigerator unit (1D) are open.
  • the two solenoid valves (7a, 7b) and the outdoor expansion valve (26) of the communication pipe (21) are closed.
  • the other refrigerant discharged from the non-inverting compressor (2A) and the first inverting compressor (2B) flows from the auxiliary gas pipe (19) to the second four-way switching valve (3B) and the first four-way compressor.
  • the outdoor gas pipe (9) After flowing through the outdoor gas pipe (9) via the switching valve (3A), it condenses in the outdoor heat exchanger (4).
  • the condensed liquid refrigerant flows through the liquid pipe (10), merges with the liquid refrigerant from the floor heating circuit (35), flows to the receiver (14), and flows through the first connecting liquid pipe (11).
  • step ST81 it is determined whether or not the condition 1 that the set temperature Tset—the indoor temperature Tr> 3 ° C. and the low-pressure refrigerant pressure LP> 392 kPa is satisfied.
  • step ST82 it is determined whether or not the condition 2 that the set temperature Tset—the indoor temperature Tr> 3 ° C. and the low-pressure refrigerant pressure L P 245 kPa is satisfied.
  • step ST83 it is determined whether or not the condition 3 that the set temperature Tset—the indoor temperature Tr is 0 ° C. and the low-pressure refrigerant pressure L P> 39 2 kPa is satisfied.
  • step ST84 it is determined whether or not the condition 4 of the set temperature Tset—the indoor temperature Tr ⁇ 0 ° C. and the low-pressure refrigerant pressure LP ⁇ 24.5 kPa is satisfied.
  • step ST81 If the condition 1 of step ST81 is satisfied, the process proceeds to step ST85, in which the capacity of the first invertor compressor (2B) or the non-inverter overnight compressor (2A) is increased, and the process returns. If condition 1 of step ST81 above is not satisfied, the condition of step ST82 is not satisfied. If condition 2 is satisfied, the process proceeds to step ST86, in which the flow rate of the outdoor fan (4F) is reduced and the process returns. In other words, since the heating capacity seems to be insufficient, the amount of heat condensed in the outdoor heat exchanger (4) is given to the indoor heat exchanger (41).
  • step ST87 the air flow of the outdoor fan (4F) is increased and the process returns. In other words, since the heating capacity is rather low, the amount of heat condensed in the indoor heat exchanger (41) is given to the outdoor heat exchanger (4).
  • step ST88 the first invertor overnight compressor (2B) or non-inverter compressor is used. Return after reducing the capacity of the compressor (2A). If condition 4 of step ST84 is not satisfied, the current compression function is satisfied, so the routine returns and the above operation is repeated.
  • the compressor capacity increase / decrease control is performed based on the second capacity control (see FIG. 6).
  • the controller (80) detects the failure and stops the operation of the compressor (2B). Then, the second inverter compressor (2C), which has not been operated, is started, and the solenoid valve (7a) is opened. As a result, the refrigerant circulates as shown in FIG. That is, a part of the refrigerant discharged from the non-inverter compressor (2A) and the second invertor compressor (2C) is condensed in the indoor heat exchanger (41) and the floor heating heat exchanger (36). .
  • the other refrigerant discharged from the non-inver evening compressor (2A) and the second inver evening compressor (2C) condenses in the outdoor heat exchanger (4) and exits from the floor heating heat exchanger (36). And flows into the receiver (14).
  • Refrigerant in the receiver (14) evaporates in the refrigeration heat exchanger (45) and the refrigeration heat exchanger (51), respectively, and is sent to the non-inverter compressor (2A) and the second inverer compressor (2C).
  • Non-invar evening compressor (2A) and 2nd invar evening compressor (2C) Is performed based on the second capacity control (see Fig. 6).
  • the second invar evening compressor (2C) can be operated in place of the non-inverter evening compressor (2A) in the same manner as above.
  • the heating / refrigeration operation can be continued.
  • the heating and refrigeration operation is not stopped and the heating capacity and the refrigeration capacity are insufficient.
  • the heating and refrigeration operation can be continued as it is.
  • the refrigeration apparatus according to the present invention is not limited to one having three compressors, but may be one having four or more compressors.
  • the “first compressor”, “second compressor”, and “third compressor” in the present invention are the non-inverter overnight compressor (2A) and the first invertor compressor (2B) of the above-described embodiment.
  • the second Invar overnight compressor (2C) may correspond to the second Invar overnight compressor (2A) or the second Invar overnight compressor (2C) of the present invention. There may be a different correspondence to correspond to "compressor”. That is, their correspondence is not particularly limited. Industrial applicability
  • the present invention is useful for a refrigeration apparatus capable of performing air conditioning and freezing.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

L'invention concerne un dispositif frigorifique pouvant conditionner l'air d'une pièce, refroidir une vitrine d'exposition et assurer le refroidissement et la congélation d'une vitrine d'exposition, et qui fonctionne sans diminution de capacité en cas de panne d'un compresseur. Ce dispositif (1) frigorifique comporte un compresseur (2A) non onduleur, un premier compresseur (2B) onduleur et un deuxième compresseur (2C) onduleur. Si le premier compresseur (2B) onduleur tombe en panne pendant un cycle de refroidissement mis en oeuvre par un échangeur (41) de chaleur pour traitement d'air intérieur, un échangeur (45) de chaleur pour conservation par le froid et un échangeur (51) de chaleur pour réfrigération, une électrovanne (7a) est ouverte dans un premier tuyau auxiliaire, ce qui permet au dispositif de continuer à fonctionner.
PCT/JP2002/006373 2001-06-26 2002-06-25 Dispositif frigorifique Ceased WO2003001129A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP02743722A EP1400766B1 (fr) 2001-06-26 2002-06-25 Dispositif frigorifique
DE60233567T DE60233567D1 (de) 2001-06-26 2002-06-25 Gefriervorrichtung
KR1020037002826A KR100544983B1 (ko) 2001-06-26 2002-06-25 냉동장치
JP2003507483A JP3953029B2 (ja) 2001-06-26 2002-06-25 冷凍装置
US10/362,625 US6698217B2 (en) 2001-06-26 2002-06-25 Freezing device
AU2002346214A AU2002346214B2 (en) 2001-06-26 2002-06-25 Freezing device

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2001192702 2001-06-26
JP2001-192702 2001-06-26

Publications (1)

Publication Number Publication Date
WO2003001129A1 true WO2003001129A1 (fr) 2003-01-03

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Application Number Title Priority Date Filing Date
PCT/JP2002/006373 Ceased WO2003001129A1 (fr) 2001-06-26 2002-06-25 Dispositif frigorifique

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US (1) US6698217B2 (fr)
EP (2) EP1400766B1 (fr)
JP (1) JP3953029B2 (fr)
KR (1) KR100544983B1 (fr)
CN (1) CN100353128C (fr)
AU (1) AU2002346214B2 (fr)
DE (2) DE60233567D1 (fr)
ES (1) ES2332127T3 (fr)
TW (1) TW548389B (fr)
WO (1) WO2003001129A1 (fr)

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EP2112444B1 (fr) 2011-03-09
KR100544983B1 (ko) 2006-01-24
TW548389B (en) 2003-08-21
JPWO2003001129A1 (ja) 2004-10-14
CN1464962A (zh) 2003-12-31
JP3953029B2 (ja) 2007-08-01
EP1400766A4 (fr) 2006-11-02
EP1400766A1 (fr) 2004-03-24
EP1400766B1 (fr) 2009-09-02
ES2332127T3 (es) 2010-01-27
US20030233836A1 (en) 2003-12-25
US6698217B2 (en) 2004-03-02
KR20030029866A (ko) 2003-04-16
EP2112444A1 (fr) 2009-10-28
DE60239430D1 (de) 2011-04-21
CN100353128C (zh) 2007-12-05
AU2002346214B2 (en) 2004-03-04
DE60233567D1 (de) 2009-10-15

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